Balanced flow cooling water jacket

ABSTRACT

A fluid jacket for a disc brake is provided that promotes a balanced flow of cooling fluid throughout the fluid jacket to most effectively remove heat from the disc brake. The fluid jacket includes an annular body configured for engagement with a friction surface. The annular body defines a plurality of concentric flow passages. The annular body further defines first and second axial flow passages in fluid communication with first and second flow passages, respectively of the plurality of concentric flow passages, with the first and second flow passage separated by a third concentric flow passage. The annular body further defines a radial flow passage extending between the first and second axial flow passages, and a fluid inlet in fluid communication with the radial flow passage.

BACKGROUND OF THE INVENTION

1. Field of the Invention

This invention relates to liquid cooled brakes and, more particularly,to a fluid jacket for use in liquid cooled brakes.

2. Disclosure of Related Art

A conventional disc brake employs two sets of friction plates that areinterleaved with each other to transmit a braking force. The frictionplates may be made from copper to enhance frictional heat transferwithin the brake. Typically, one set of plates is fixed against rotationrelative to a stationary body such as a brake housing, but is axiallymovable relative to the stationary body. The other set of plates rotatewith a rotating body such as a driven shaft, but are also axiallymoveable relative to the rotating body. An actuator is employed to bringthe plates into engagement through which the rotating body is braked.

Braking a rotating body results in a conversion of mechanical energy toheat energy. In many instances, it is desirable to provide for effectiveremoval of some of the heat developed from the brake structure. Onemethod of removing heat from a disc brake is to use a liquid to cool thebrake structure and transfer heat out of the brake structure. In oneconventional form of a liquid cooled disc brake, one set of the frictionplates define fluid jackets for circulating a cooling fluid therethroughto reduce the heat generated in the brake by the frictional engagementof the friction plates.

One conventional fluid jacket has a plurality of concentric flowpassages and a radial flow passage that is in fluid communication witheach of the concentric flow passages. A fluid inlet and outletcommunicate with the radial flow passage. In theory, fluid issimultaneously delivered to each of the concentric passages afterentering the radial flow passage from the fluid inlet. In practice,however, it has been determined that the flow of fluid is uneven withinand among the concentric passages. In particular, fluid flow in theradially inner concentric passages is relatively high, while fluid flowin the radially outer concentric passages is relatively low. Effectivefluid flow in the radially outer concentric passages is especiallyimportant since more heat is generated toward the radially outer portionof the friction plate which rotates at a faster speed than the radiallyinner portion of the plate.

The inventors herein have recognized a need for a fluid jacket for adisc brake that will minimize and/or eliminate one or more of theabove-identified deficiencies.

SUMMARY OF THE INVENTION

The present invention provides a fluid jacket for a disco brake thatresults in improved fluid flow.

A fluid jacket in accordance with the present invention includes anannular body configured for engagement with a friction surface. Theannular body defines a plurality of concentric flow passages. Theannular body further defines a first axial flow passage in fluidcommunication with a first flow passage of the plurality of concentricflow passages. The annular body further defines a second axial flowpassage in fluid communication with a second flow passage of theplurality of concentric flow passages. The second flow passage isseparated from the first flow passage by a third flow passage of theplurality of concentric flow passages. The annular body further definesa radial flow passage extending between the first and second axial flowpassages and a fluid inlet in communication with the radial flowpassage.

A fluid jacket in accordance with the present invention represents asignificant improvement relative to conventional fluid jackets used indisc brakes. In particular, the inventive fluid jacket significantlyimproves fluid flow among the concentric flow passages of the fluidjacket promoting a more balanced fluid flow among the passages. As aresult, the fluid jackets more effectively dissipate heat from thebrake.

These and other advantages of this invention will become apparent to oneskilled in the art from the following detailed description and theaccompanying drawings illustrating features of this invention by way ofexample.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a cross-sectional view of a brake incorporating a fluid jacketin accordance with the present invention.

FIG. 2 is an enlarged cross-sectional view of a fluid jacket inaccordance with the present invention.

FIG. 3 is a plan view of a fluid jacket in accordance with the presentinvention.

DETAILED DESCRIPTION OF EMBODIMENTS OF THE INVENTION

Referring now to the drawings wherein like reference numerals are usedto identify identical components in the various views, FIG. 1illustrates a brake 10 in accordance with the present invention. Brake10 may be provided for heavy duty industrial use (e.g., on oil drillingequipment). Brake 10 includes a housing 12, two sets of friction plates14A-B, 16, and an end cap assembly 18.

Housing 12 provides structural support to the other components of brake10. Housing 12 may be made from conventional metals, metal alloys and/orplastics. Housing 12 is disposed about a driven shaft 20 and may becentered about the rotational axis 22 of the shaft 20. Housing 12 may besubstantially circular in shape and unitary in construction. Housing 12defines axially extending bores 24, 26 at either end configured toreceive fasteners 28, 30 used to connect a friction plate 14 and end capassembly 18, respectively, to housing 12. Housing 12 also defines aplurality of radial openings 32 sized for receipt of hoses andconnectors (not shown).

Friction plates 14A, 14B are provided to transmit a braking torque tofriction plate 16 and shaft 20 upon engagement of plates 14A, 14B, 16.Friction plate 14A is fixed to housing 12 by fasteners 28 extendingthrough friction plate 14A. Friction plate 14B is coupled to housing 12through the use of spline teeth 34, 36 on a radially inner surface ofhousing 12 and a radially outer surface of plate 14B, respectively. Inthis manner, plate 14B is fixed against rotation relative to housing 12,but is axially movable relative to housing 12. Although only one movableplate 14B is shown in the illustrated embodiment, it should be readilyunderstood that additional plates 14B (and friction plates 16) could beinterleaved and used to provide increased braking torque). Each offriction plates 14A, 14B includes one or more plates 38 and a fluidjacket 40 in accordance with the present invention (described in greaterdetail hereinbelow). Plates 38 are conventional in the art and may bemade from a variety of conventional metals and metal alloys includingiron or copper. Plates 38 may be connected to one or both sides of eachfluid jacket 40 using fasteners 42 such as bolts or screws or pins.

Friction plate 16 is provided to transfer braking torque from frictionplates 14A, B to shaft 20. Friction plate 16 may be made fromconventional metals and metal alloys such as iron and copper. Plate 16is coupled to a hub 44 fixed to shaft 20 (or directly to shaft 20)through the use of spline teeth 46, 48 on a radially inner surface ofplate 16 and a radially outer surface of hub 44 (or shaft 20),respectively. Plate 16 may include a conventional friction material 50connected to each side of plate 16 by fasteners 52 such as bolts orscrews. Again, although only plate 16 is shown in the illustratedembodiment, it should be understood that additional plates 16 could beinterleaved with additional plates 14B to increase braking torque.

End cap assembly 18 closes one end of housing 12 (opposite frictionplate 14A) and provides support for brake actuators. In the illustratedembodiment, end cap assembly 18 includes a plate 54 that is annular inconstruction and which is fastened to housing 12 using one morefasteners 30. Plate 54 defines an annular recess 56 configured toreceive an expandable bladder 58 that bears against a pressure plate 60.Plate 54 also defines an axial bore 62 through which pneumatic orhydraulic fluid is provided to bladder 58 via a hose (not shown) and astepped diameter bore 64 through which a fastener 66 extends. Fastener66 is surrounded by a spring 68 disposed in a larger diameter portion ofbore 64 and extends through plate 54 into friction plate 14B. When fluidis supplied to bladder 58, bladder 58 expands and urges pressure plate60 in an axial direction against the force of spring 68 to compress, andcause engagement of, friction plates 14A-B, 16. When fluid pressure isremoved from bladder 58, spring 68 biases friction plate 14B in a secondaxial direction to its original position. Although the illustratedembodiment employs a single actuator acting as a tension brake, itshould be understood that the fluid jackets 40 described herein could beemployed in a variety of brakes.

Referring now to FIGS. 2-3, a fluid jacket 40 in accordance with thepresent invention will be described and illustrated. Jacket 40 isprovided to allow for circulation of a cooling liquid such as water oranother conventional liquid within brake 10 to allow for transfer offrictional heat generated within brake 10. Jacket 40 includes an annularbody 70 that defines a fluid manifold through which liquid circulatesand provides a surface on which plates 38 (See FIG. 1) are mounted. Body70 may define a plurality of concentric flow passages 72, 74, 76, 78,80, 82, 84 a plurality of axial flow passages 86, 88, 90, 92 a pluralityof radial flow passage 94, 96 a fluid inlet 98 and a fluid outlet 100.

Concentric flow passages 72, 74, 76, 78, 80, 82, 84, are provided forcirculation of a cooling liquid adjacent to plates 38 and along theentire radial and circumferential extent of plates 38. In theillustrated embodiment, flow passages 72, 74, 76,78, 80, 82, 84 aredisposed on only one axial face of body 70 of jacket 40. Referring toFIG. 1, however, it should be understood that similar passages may beformed on the opposite of body 70 of jacket 40 depending on the locationof the friction plates 14A, 14B containing jacket 40 (e.g., if frictionplates 16 were disposed on either side of friction plate 14B). It shouldalso be understood that, although the illustrated embodiment of theinvention shows seven (7) concentric flow passages 72, 74, 76, 78, 80,82, 84, the number of flow passages could vary. In the illustratedembodiment, flow passage 72 comprises the radially innermost concentricflow passage while flow passage 84 comprises the radially outermostconcentric flow passage. Flow passages 74, 76, 78, 80, 82 are disposedbetween flow passage 72, 84. Referring to FIG. 3, flow passages 72, 74,76, 78, 80, 82, 84 are defined by concentric annular walls, such as wall102, and may be in fluid communication with each other at partitions 104that are made in walls 102 at diametrically opposite positions withinfluid jacket 40. The radial width of the flow passages may be equal asshown in the illustrated embodiment.

Axial flow passages 86, 88, 90, 92 provide fluid communication betweenconcentric flow passages 72, 74, 76, 78, 80, 82, 84 and radial flowpassage 94, 96, respectively. Axial flow passages 86, 88, 90, 92, areeach in direct fluid communication with at least one concentric flowpassage 72, 74, 76, 78, 80, 82, 84. In the illustrated embodiment, axialflow passages, 86, 90, are in fluid communication with the radiallyoutermost concentric flow passage 84 and are also in fluid communicationwith the flow passage 82 disposed radially inwardly of passage 84. Adiameter of each of axial flow passages 86, 90 extends across the fullradial length of concentric flow passage 84 and across only a portion(approximately one-half in the illustrated embodiment) of the radiallength of concentric flow passage 82. Axial flow passages 88, 92, are influid communication with adjacent concentric flow passages 74, 76. Adiameter of each of axial flow passages 88, 92 extends across only aportion (less than one-half in the illustrated embodiment) of the radiallength of each of concentric flow passages 74, 76. The diameters ofaxial flow passages 88, 92, are smaller than the diameters of axial flowpassage 86, 90. In the illustrated embodiment, no portion of radiallyinnermost concentric flow passage 72 or flow passages 78, 80 are indirect fluid communication with any of axial flow passages 86, 88, 90,92. Accordingly, the concentric flow passages 74, 76, and 82, 84, withwhich the axial flow passages, 88, 92, and 86, 90, respectively, are indirect fluid communication are separated by concentric flow passages 78,80.

Radial flow passages 94, 96 provides fluid communication between axialflow passages 86, 88, 90, 92, and fluid inlet 98 and outlet 100. Radialflow passages 94, 96 extend between axial flow passages 86, 90 and 88,92, respectively. The diameters of radial flow passages 94, 96, may beconstant between axial flow passages 86, 90 and 88, 92, respectively,.Radial flow passage 94, 96 may be located at diametrically oppositelocations within jacket 40 and may be axially aligned with partitions104 in annular walls 102 forming concentric flow passages 72, 74, 76,78, 80, 82, 84.

Fluid inlet 98 and fluid outlet 100 are provided for the introductionand exit of fluid from fluid jacket 40. Inlet 98 and outlet 100 may belocated at radially outer points on jacket 40. Inlet 98 and outlet 100may have a diameter greater than the diameter of radial flow passages94, 96 and may be sized, and threaded, to receive a fluid connector (notshown).

A fluid jacket in accordance with the present invention represents asignificant improvement relative to conventional fluid jackets. Inparticular, the inventive fluid jacket significantly improves andoptimizes fluid flow among the concentric flow passages of the fluidjacket promoting a more balanced fluid flow among the passages. As aresult, the fluid jackets more effectively dissipate heat from thebrake.

While the invention has been shown and described with reference to oneor more particular embodiments thereof, it will be understood by thoseof skill in the art that various changes and modifications can be madewithout departing from the spirit and scope of the invention.

1. A fluid jacket for a disc brake, comprising: an annular bodydefining: a plurality of concentric flow passages; a first axial flowpassage in fluid communication with a first flow passage of saidplurality of concentric flow passages; a second axial flow passage influid communication with a second flow passage of said plurality ofconcentric flow passages, said second flow passage separated from saidfirst flow passage by a third flow passage of said plurality ofconcentric flow passages; a radial flow passage extending between saidfirst and second axial flow passages; and, a fluid inlet incommunication with said radial flow passage.
 2. The fluid jacket ofclaim 1 wherein said first flow passage of said plurality of concentricflow passages comprises a radially outermost flow passage of saidplurality of concentric flow passages.
 3. The fluid jacket of claim 1wherein a diameter of said first axial flow passage extends across aradial length of said first flow passage of said plurality of concentricflow passages.
 4. The fluid jacket of claim 1 wherein said first axialflow passage is in fluid communication with said third flow passage ofsaid plurality of concentric flow passages.
 5. The fluid jacket of claim4 wherein a diameter of said first axial flow passage extends acrossonly a portion of a radial length of said third flow passage of saidplurality of concentric flow passages.
 6. The fluid jacket of claim 1wherein said first axial flow passage is in fluid communication with afourth flow passage of said plurality of concentric flow passages, saidfourth flow passage disposed radially outwardly of said third flowpassage.
 7. The fluid jacket of claim 6 wherein a diameter of said firstaxial flow passage extends across only a portion of a radial length ofsaid fourth flow passage of said plurality of concentric flow passages.8. The fluid jacket of claim 1 wherein a diameter of said second axialflow passage extends across only a portion of a radial length of saidsecond flow passage of said plurality of concentric flow passages. 9.The fluid jacket of claim 1 wherein said second axial flow passage is influid communication with said third flow passage of said plurality ofconcentric flow passages.
 10. The fluid jacket of claim 9 wherein adiameter of said second axial flow passage extends across only a portionof a radial length of said third flow passage of said plurality ofconcentric flow passages.
 11. The fluid jacket of claim 1 wherein saidsecond axial flow passage is in fluid communication with a fourth flowpassage of said plurality of concentric flow passages, said fourth flowpassage disposed radially inwardly of said third flow passage.
 12. Thefluid jacket of claim 11 wherein a diameter of said second axial flowpassage extends across only a portion of a radial length of said fourthflow passage of said plurality of concentric flow passages.
 13. Thefluid jacket of claim 1, wherein said second flow passage of saidplurality of concentric flow passages is disposed radially inwardly fromsaid first flow passage of said plurality of concentric flow passagesand a fourth flow passage of said plurality of concentric flow passagesis disposed radially inwardly of from said second flow passage of saidplurality of concentric flow passages.
 14. The fluid jacket of claim 1wherein said second axial flow passage is smaller in diameter than saidfirst axial flow passage.
 15. The fluid jacket of claim 1 wherein afourth flow passage of said plurality of concentric flow passageseparates said first and second flow passages of said plurality ofconcentric flow passages.
 16. The fluid jacket of claim 1 wherein adiameter of said radial flow passage is constant between said first andsecond axial flow passages.
 17. A brake, comprising: a stationaryhousing disposed about a driven shaft, said driven shaft rotating abouta rotational axis; a first friction plate coupled to said housing andfixed against rotation relative to said housing; a second friction platecoupled to said driven shaft for rotation therewith and for axialmovement relative to said driven shaft; a pressure plate configured forselective movement in a first axial direction towards said first andsecond friction plates; wherein said first friction plate defines afluid jacket including an annular body defining a plurality ofconcentric flow passages; a first axial flow passage in fluidcommunication with a first flow passage of said plurality of concentricflow passages; a second axial flow passage in fluid communication with asecond flow passage of said plurality of concentric flow passages, saidsecond flow passage separated from said first flow passage by a thirdflow passage of said plurality of concentric flow passages; a radialflow passage extending between said first and second axial flowpassages; and, a fluid inlet in communication with said radial flowpassage.
 18. The brake of claim 17, wherein one of said first and secondaxial flow passages is in communication with said third flow passage ofsaid plurality of concentric flow passages.
 19. The brake of claim 18wherein another of said first and second axial flow passages is incommunication with a fourth flow passage of said plurality of concentricflow passages.
 20. The brake of claim 17 wherein said second axial flowpassage is smaller in diameter than said first axial flow passage.